Hydraulic energy transfer system with filtering system

ABSTRACT

A system includes a hydraulic energy transfer system configured to exchange pressures between a first fluid and a second fluid, wherein pressure of the first fluid is greater than pressure of the second fluid. The system also includes a lubrication system coupled to the hydraulic energy transfer system and configured to pump or direct a lubrication fluid into the hydraulic energy transfer system.

BACKGROUND

This section is intended to introduce the reader to various aspects ofart that may be related to various aspects of the present invention,which are described and/or claimed below. This discussion is believed tobe helpful in providing the reader with background information tofacilitate a better understanding of the various aspects of the presentinvention. Accordingly, it should be understood that these statementsare to be read in this light, and not as admissions of prior art.

The subject matter disclosed herein relates to fluid handling equipmentand, in particular, fluid handling equipment for applications involvinga variety of fluids. Some of these fluids may include solids (e.g.,particles, powders, debris, particulates) and/or contaminants (e.g.,viscosifiers, chemical additives, or any fluids that are undesirable forbearing lubrication), which may interfere with the operation of thefluid handling equipment. Fluid handling equipment may be used in avariety of applications. For example, fluid handling equipment may beused in hydraulic fracturing, in a drilling application (circulatingdrilling fluids and/or mud), or similar processes. In particular, wellcompletion operations in the oil and gas industry often involvehydraulic fracturing (commonly referred to as fracking or fracing) toincrease the release of oil and gas in rock formations. Hydraulicfracturing involves pumping a fluid containing a combination of water,chemicals, and proppant (e.g., sand, ceramics) into a well at highpressures. The high-pressures of the fluid increases crack size andpropagation through the rock formation releasing more oil and gas, whilethe proppant prevents the cracks from closing once the fluid isdepressurized.

Fracturing operations use a variety of rotating equipment, such as ahydraulic energy transfer system, to handle a variety of fluids that mayinclude solids (e.g., particles, powders, debris, particulates) and/orcontaminants (e.g., viscosifiers, chemical additives, or any fluids thatare undesirable for bearing lubrication). In certain circumstances, thesolids may prevent the rotating components of the rotating equipmentfrom rotating. Thus, the rotating equipment may be taken out of serviceto enable the solids to be removed and/or enable the rotating componentsto be rotated. In some situations, lubrication systems may facilitatethe rotation of the rotating components within the hydraulic energytransfer system. However, the fluids utilized within the lubricationsystems may include additional solids or contaminants, such asparticles, powders, debris, and so forth, and these solids orcontaminants may have negative impacts on performance of the rotatingcomponents (e.g., decreased performance/efficiency, abrasion tocomponents, etc.).

BRIEF DESCRIPTION

In one embodiment, a system includes a hydraulic energy transfer systemconfigured to exchange pressures between a first fluid and a secondfluid, wherein pressure of the first fluid is greater than pressure ofthe second fluid. The system also includes a lubrication system coupledto the hydraulic energy transfer system and configured to pump or directa lubrication fluid into the hydraulic energy transfer system.

In another embodiment, a system includes a hydraulic energy transfersystem configured to exchange pressures between a first fluid and asecond fluid, wherein pressure of the first fluid is greater thanpressure of the second fluid. The system includes a lubrication systemcoupled to the hydraulic energy transfer system and configured to pumpor direct a lubrication fluid into the hydraulic energy transfer system.The system includes a filtration system coupled to the hydraulic energytransfer system and configured to filter the lubrication fluid beforethe lubrication fluid enters the hydraulic energy transfer system. Thesystem includes one or more valves and one or more pumps disposed alongfluid flow paths of the system. The system also includes a controllerprogrammed to control the one or more valves and/or the one or morepumps of the system to selectively route the lubrication fluid into thehydraulic energy transfer system based on operating condition of thesystem.

In another embodiment, a system includes a hydraulic energy transfersystem configured to exchange pressures between a first fluid and asecond fluid, wherein pressure of the first fluid is greater thanpressure of the second fluid. The system includes a lubrication systemcoupled to the hydraulic energy transfer system and the lubricationsystem includes a dedicated pump to direct a lubrication fluid into thehydraulic energy transfer system. The system includes a filtrationsystem coupled to the hydraulic energy transfer system and configured tofilter the lubrication fluid before the lubrication fluid enters thehydraulic energy transfer system, wherein the lubrication fluid includesa fraction of the first fluid or a fluid from a fluid supply sourceexternal to the hydraulic energy transfer system. The system alsoincludes a controller programmed to control one or more valves and/orone or more pumps disposed along fluid flow paths of the system toselectively route the lubrication fluid into the hydraulic energytransfer system based on an operating condition of the system.

BRIEF DESCRIPTION OF THE DRAWINGS

Various features, aspects, and advantages of the present invention willbecome better understood when the following detailed description is readwith reference to the accompanying figures in which like charactersrepresent like parts throughout the figures, wherein:

FIG. 1 is a schematic diagram of an embodiment of a frac system with ahydraulic energy transfer system;

FIG. 2 is an exploded perspective view of an embodiment of the hydraulicenergy transfer system of FIG. 1, illustrated as a rotary isobaricpressure exchanger (IPX) system;

FIG. 3 is a schematic diagram of an embodiment of the IPX system of FIG.2, illustrating a filtration system;

FIG. 4 is a schematic diagram of an embodiment of the IPX system of FIG.2, illustrating an embodiment of an integrated filtration system with aplurality of filters;

FIG. 5 is a schematic diagram of an embodiment of the integratedfiltration system of FIG. 4, illustrating a settling filtration system;

FIG. 6 is a schematic diagram of an embodiment of the filtration systemof FIG. 3, illustrating a centrifugal separation filtration system;

FIG. 7 is a schematic diagram of an embodiment of the IPX system of FIG.2, illustrating a filtration system disposed within the rotor.

FIG. 8 is a block diagram of an embodiment of the IPX system of FIG. 2coupled to a lubrication system having a dedicated lubrication fluidsupply source;

FIG. 9 is a block diagram of an embodiment of the IPX system of FIG. 2coupled to a lubrication having a dedicated pump to direct thelubrication fluid;

FIG. 10 is a block diagram of an embodiment of a controller operativelycoupled to a lubrication system;

FIG. 11 is a partial circuit diagram of lubrication fluid, illustratingrouting of the lubrication fluid; and

FIG. 12 is a schematic diagram of an embodiment of the IPX system ofFIG. 2 coupled to a lubrication system.

DETAILED DESCRIPTION OF SPECIFIC EMBODIMENTS

One or more specific embodiments of the present invention will bedescribed below. These described embodiments are only exemplary of thepresent invention. Additionally, in an effort to provide a concisedescription of these exemplary embodiments, all features of an actualimplementation may not be described in the specification. It should beappreciated that in the development of any such actual implementation,as in any engineering or design project, numerousimplementation-specific decisions must be made to achieve thedevelopers' specific goals, such as compliance with system-related andbusiness-related constraints, which may vary from one implementation toanother. Moreover, it should be appreciated that such a developmenteffort might be complex and time consuming, but would nevertheless be aroutine undertaking of design, fabrication, and manufacture for those ofordinary skill having the benefit of this disclosure.

As discussed above, clean lubrication fluid may be important to theoperation of rotating equipment, such as rotating components within ahydraulic energy transfer system (e.g., rotary pressure exchanger). Asmall amount of particulates or contaminants in the lubrication fluid orlube may affect the equipment performance causing the rotatingcomponents to stall, causing wearing or abrasion of the rotatingcomponents, or otherwise adversely affecting performance. With this inmind, the present embodiments are directed to systems and methods toprovide a clean/suitable fluid for lube flow and fluid bearings andseals. A dedicated external pump may be used for providing the lubeflow, and a filtration system may filter or clean only a small portionof the total fluid flow into the rotating equipment, as compared to theentire fluid flow. As such, the present embodiments may offeradvantages, such as cost saving, easier maintenance, and energy savingas comparing to filtering the entire fluid flow.

As discussed in detail below, the embodiments disclosed herein generallyrelate to fluid handling equipment that may be used in many applicationsto handle a variety of fluids that may include solids (e.g., particles,powders, debris, particulates) and/or contaminants (e.g., viscosifiers,chemical additives, or any fluids that are undesirable for bearinglubrication). For example, fluid handling equipment may be used infracturing application, such as in a hydraulic fracturing system.Hydraulic fracturing systems and operations use a variety of rotatingequipment, such as a hydraulic energy transfer system, to handle avariety of fluids. As noted above, lubrication systems may facilitatethe rotation of the rotating components within the hydraulic energytransfer system. However, in some situations, the fluids utilized withinthe lubrication systems may include additional solids, such as such asparticles, powders, debris, and so forth. Accordingly, the disclosedembodiments relate to filtering a lubrication fluid that may be usedwithin a lubrication system of the hydraulic energy transfer system.

A frac system (or hydraulic fracturing system) includes a hydraulicenergy transfer system that transfers work and/or pressure between firstand second fluids, such as a pressure exchange fluid (e.g., asubstantially proppant-free fluid, such as water) and a hydraulicfracturing fluid (e.g., a proppant-laden frac fluid). The hydraulicenergy transfer system may also be described as a hydraulic protectionsystem, hydraulic buffer system, or a hydraulic isolation system,because it may block or limit contact between a frac fluid and varioushydraulic fracturing equipment (e.g., high-pressure pumps) whileexchanging work and/or pressure with another fluid. The hydraulic energytransfer system may include a hydraulic turbocharger or a hydraulicpressure exchange system, such as a rotating isobaric pressure exchanger(IPX).

In certain embodiments, the IPX may include one or more chambers (e.g.,1 to 100) to facilitate pressure transfer and equalization of pressuresbetween volumes of first and second fluids (e.g., gas, liquid, ormulti-phase fluid). For example, one of the fluids (e.g.., the fracfluid) may be a multi-phase fluid, which may include gas/liquid flows,gas/solid particulate flows, liquid/solid particulate flows,gas/liquid/solid particulate flows, or any other multi-phase flow. Insome embodiments, the pressures of the volumes of first and secondfluids may not completely equalize. Thus, in certain embodiments, theIPX may operate isobarically, or the IPX may operate substantiallyisobarically (e.g., wherein the pressures equalize within approximately+/−1, 2, 3, 4, 5, 6, 7, 8, 9, or 10 percent of each other). In certainembodiments, a first pressure of a first fluid (e.g., pressure exchangefluid) may be greater than a second pressure of a second fluid (e.g.,frac fluid). For example, the first pressure may be betweenapproximately 5,000 kPa to 25,000 kPa, 20,000 kPa to 50,000 kPa, 40,000kPa to 75,000 kPa, 75,000 kPa to 100,000 kPa or greater than the secondpressure. Thus, the IPX may be used to transfer pressure from a firstfluid (e.g., pressure exchange fluid) at a higher pressure to a secondfluid (e.g., frac fluid) at a lower pressure. In some embodiments, theIPX may transfer pressure between a first fluid (e.g., pressure exchangefluid, such as a first proppant free or substantially proppant freefluid) and a second fluid that may be highly viscous and/or containproppant (e.g., frac fluid containing sand, solid particles, powders,debris, ceramics). In operation, the hydraulic energy transfer systemhelps to block or limit contact between the second proppant containingfluid and various fracturing equipment (e.g., high-pressure pumps)during fracturing operations. By blocking or limiting contact betweenvarious fracturing equipment and the second proppant containing fluid,the hydraulic energy transfer system increases the life/performancewhile reducing abrasion/wear of various fracturing equipment (e.g.,high-pressure pumps). Moreover, it may enable the use of cheaperequipment in the fracturing system by using equipment (e.g.,high-pressure pumps) not designed for abrasive fluids (e.g., frac fluidsand/or corrosive fluids).

With the foregoing in mind, FIG. 1 is a schematic diagram of anembodiment of a fracturing equipment or a frac system 10 with ahydraulic energy transfer system. It should be noted that the hydraulicenergy transfer system discussed herein may also be used in any suitableapplications to handle a variety of fluids, and the use of the hydraulicenergy transfer system in fracturing application is discussed herein asan example. In operation, the frac system 10 enables well completionoperations to increase the release of oil and gas in rock formations.Specifically, the frac system 10 pumps a frac fluid containing acombination of water, chemicals, and proppant (e.g., sand, ceramics,etc.) into a well at high-pressures. The high-pressures of the fracfluid increases crack size and propagation through the rock formation,which releases more oil and gas, while the proppant prevents the cracksfrom closing once the frac fluid is depressurized. As illustrated, thefrac system 10 includes a high-pressure pump 12 and a low-pressure pump14 coupled to a hydraulic energy transfer system 16 (e.g., a hydraulicturbocharger or IPX). In operation, the hydraulic energy transfer system16 transfers pressures between a first fluid 18 (e.g., proppant freefluid) pumped by the high-pressure pump 12 and a second fluid 20 (e.g.,proppant containing fluid or frac fluid) pumped by the low-pressure pump14. In this manner, the hydraulic energy transfer system 16 blocks orlimits wear on the high-pressure pump 12, while enabling the frac system10 to pump a high-pressure frac fluid 22 into a downstream application24, such as a well, and to pump a low-pressure frac fluid 23 (e.g.,proppant free fluid or frac fluid) out of the hydraulic energy transfersystem 16.

In an embodiment, the hydraulic energy transfer system 16 may include ahydraulic turbocharger 26, the first fluid 18 (e.g., high-pressureproppant free fluid) enters a first side of the hydraulic turbocharger26 and the second fluid 20 (e.g., low-pressure frac fluid) may enter thehydraulic turbocharger 26 on a second side. In operation, the flow ofthe first fluid 18 drives a first turbine coupled to a shaft. As thefirst turbine rotates, the shaft transfers power to a second turbinethat increases the pressure of the second fluid 20, which drives thesecond fluid 20 out of the hydraulic turbocharger 26 and down thedownstream application 24 (e.g., a well) during fracturing operations.In an embodiment, the hydraulic energy transfer system 16 may include anisobaric pressure exchanger (IPX) 28, the first fluid 18 (e.g.,high-pressure proppant free fluid) enters a first side of the hydraulicenergy transfer system 16 where the first fluid contacts the secondfluid 20 (e.g., low-pressure frac fluid) entering the IPX 28 on a secondside. The contact between the fluids enables the first fluid 18 toincrease the pressure of the second fluid 20, which drives the secondfluid 20 out of the IPX 28 and down the downstream application 24 (e.g.,a well) for fracturing operations. The first fluid 18 similarly exitsthe IPX 28, but at a low-pressure after exchanging pressure with thesecond fluid 20.

As used herein, the IPX 28 may be generally defined as a device thattransfers fluid pressure between a high-pressure inlet stream and alow-pressure inlet stream at efficiencies in excess of approximately50%, 60%, 70%, or 80% without utilizing centrifugal technology. In thiscontext, high pressure refers to pressures greater than the lowpressure. The low-pressure inlet stream of the IPX 28 may be pressurizedand exit the IPX 28 at high pressure (e.g., at a pressure greater thanthat of the low-pressure inlet stream), and the high-pressure inletstream may be depressurized and exit the IPX 28 at low pressure (e.g.,at a pressure less than that of the high-pressure inlet stream).Additionally, the IPX 28 may operate with the high-pressure fluiddirectly applying a force to pressurize the low-pressure fluid, with orwithout a fluid separator between the fluids. Examples of fluidseparators that may be used with the IPX 28 include, but are not limitedto, pistons, bladders, diaphragms and the like. In certain embodiments,IPX 28 may include one or more rotary devices (e.g., rotary IPX), suchas those manufactured by Energy Recovery, Inc. of San Leandro, Calif.The rotary IPX may not have any separate valves, since the effectivevalving action is accomplished internal to the device via the relativemotion of a rotor with respect to end covers, as described in detailbelow with respect to FIG. 2. Rotary IPXs may be designed to operatewith internal pistons to isolate fluids and transfer pressure withrelatively little mixing of the inlet fluid streams. In certainembodiments, IPX 28 may include one or more reciprocating rotary IPXsthat may each include a piston moving back and forth in a cylinder fortransferring pressure between the fluid streams. One or more IPXs 28 maybe used in the disclosed embodiments, such as, but not limited to,rotary IPX(s), reciprocating IPX(s), or any combination thereof. Inaddition, the IPX 28 may be disposed on a skid separate from the othercomponents of a fluid handling system (e.g., fracturing equipment or thefrac system 10), which may be desirable in situations in which the IPX28 is added to an existing fluid handling system.

FIG. 2 is an exploded view of an embodiment of the IPX 28 (e.g., arotary IPX). In the illustrated embodiment, the IPX 28 may include agenerally cylindrical body portion 40 that includes a housing 42 and arotor 44. The IPX 28 may also include two end structures 46 and 48 thatinclude manifolds 50 and 52, respectively. Manifold 50 includes inletand outlet ports 54 and 56 and manifold 52 includes inlet and outletports 60 and 58. For example, inlet port 54 may receive a high-pressurefirst fluid and the outlet port 56 may be used to route a low-pressurefirst fluid away from the IPX 28. Similarly, inlet port 60 may receive alow-pressure second fluid and the outlet port 58 may be used to route ahigh-pressure second fluid away from the IPX 28. The end structures 46and 48 include generally flat end plates 62 and 64, respectively,disposed within the manifolds 50 and 52, respectively, and adapted forfluid sealing contact with the rotor 44. The rotor 44 may be cylindricaland disposed in the housing 42, and is arranged for rotation about alongitudinal axis 66 of the rotor 44. The rotor 44 may have a pluralityof channels 68 extending substantially longitudinally through the rotor44 with openings 70 and 72 at each end arranged symmetrically about thelongitudinal axis 66. The openings 70 and 72 of the rotor 44 arearranged for hydraulic communication with the end plates 62 and 64, andinlet and outlet apertures 74 and 76, and 78 and 80, in such a mannerthat during rotation they alternately hydraulically expose fluid at highpressure and fluid at low pressure to the respective manifolds 50 and52. The inlet and outlet ports 54, 56, 58, and 60, of the manifolds 50and 52 form at least one pair of ports for high-pressure fluid in oneend element 46 or 48, and at least one pair of ports for low-pressurefluid in the opposite end element, 48 or 46. The end plates 62 and 64,and inlet and outlet apertures 74 and 76, and 78 and 80 are designedwith perpendicular flow cross sections in the form of arcs or segmentsof a circle.

With respect to the IPX 28, a plant operator has control over the extentof mixing between the first and second fluids 18 and 20, which may beused to improve the operability of the fluid handling system (e.g.,fracturing equipment or the frac system 10). For example, varying theproportions of the first and second fluids 18 and 20 entering the IPX 28allows the plant operator to control the amount of fluid mixing withinthe fluid handling system. Three characteristics of the IPX 28 that mayaffect mixing are: (1) the aspect ratio of the rotor channels 68, (2)the short duration of exposure between the first and second fluids 18and 20, and (3) the creation of a fluid barrier (e.g., an interface)between the first and second fluids within the rotor channels 68. First,the rotor channels 68 are generally long and narrow, which stabilizesthe flow within the IPX 28. In addition, the first and second fluids 18and 20 may move through the channels 68 in a plug flow regime with verylittle axial mixing. Second, in certain embodiments, at a rotor speed ofapproximately 1200 rotation per minute (RPM), the time of contactbetween the first and second fluids 18 and 20 may be less thanapproximately 0.15 seconds, 0.10 seconds, or 0.05 seconds, which againlimits mixing of the streams 18 and 30. Third, a small portion of therotor channel 68 is used for the exchange of pressure between the firstand second fluids 18 and 20. Therefore, a volume of fluid remains in thechannel 68 as a barrier between the first and second fluids 18 and 20.All these mechanisms may limit mixing within the IPX 28.

In addition, because the IPX 28 is configured to be exposed to the firstand second fluids 18 and 20, certain components of the IPX 28 may bemade from materials compatible with the components of the first andsecond fluids 18 and 20. In addition, certain components of the IPX 28may be configured to be physically compatible with other components ofthe fluid handling system (e.g., fracturing equipment or the frac system10). For example, the ports 54, 56, 58, and 60 may comprise flangedconnectors to be compatible with other flanged connectors present in thepiping of the fluid handling system. In other embodiments, the ports 54,56, 58, and 60 may comprise threaded or other types of connectors.

FIG. 3 is a schematic diagram of an embodiment of the IPX 28 (e.g.,rotary IPX) of FIG. 2 coupled to a filtration system 90. In theillustrated embodiment, the IPX 28 is orientated with respect to anaxial axis 92, a radial axis 94, and a circumferential axis 96. Inoperation, the IPX 28 uses a rotor 100 (e.g., the rotor 44 in FIG. 2) totransfer pressure from the first fluid 18, pumped by the high-pressurepump 12, to the second fluid 20, pumped by the lower pressure pump 14.The first fluid 18 and/or the second fluid 20 may be a highly viscous orparticulate laden fluid. Over time, these fluids 18 and 20 may slow orblock the rotation of the rotor 100 or may even block startup of the IPX28 with fluid leftover from previous operations. Accordingly, the IPX 28includes the lubrication system 98 that may pump (e.g., via a pump, suchas the high pressure pump 12 or a dedicated pump as will be discussed inFIGS. 8-10) or direct a lubrication fluid through the IPX 28 before,during, and/or after operation of the IPX 28 to lubricate the rotatingcomponents of the IPX 28 during operation.

In certain embodiments, the lubrication system 98 is fluidly coupled tothe filtration system 90 that filters out particulates suspended withinthe lubrication fluid before the lubrication fluid is supplied to theIPX 28. In certain embodiments, the filtration system 90 receives asmall fraction of high-pressure fluid 18 from the high-pressure pump 12,such as a small amount of high-pressure proppant free fluid (e.g.,water). Accordingly, the filtration system 90 may filter the smallfraction of the high-pressure fluid (e.g., the first fluid 18) flowinginto the IPX 28 as lubrication fluid.

As may be appreciated, clean lubrication fluid as indicated by arrows 91may be routed into the IPX 28 via a lubrication flow channel that isseparate from the total flow of the high pressure fluid (e.g., the firstfluid 18). The separate lubrication channel may be external an IPXhousing 102 (e.g., the housing 42), or may be integral to the IPXhousing 102, as depicted within the embodiments illustrated in FIGS.4-7. The separate channel allows the filtration system 90 to operateindependently from or concurrently with the steady state operations ofthe IPX 28. For example, the lubrication system 98 may provide the IPX28 with the clean lubrication fluid before and/or during steady stateoperations of the IPX 28.

In certain embodiments, the IPX 28 includes a controller 104 coupled toa processor 106 and a memory 108 that stores instructions executable bythe processor 106 for controlling the filtration system 90 and/or thelubrication system 98. For example, the controller 104 may control oneor more valves (e.g., electronic actuators that open and close thevalves), filters, flow rates, and so forth of the filtration system 90and/or the lubrication system 98. Furthermore, the controller 104 maycommunicate with one or more sensors disposed throughout the hydraulicenergy transfer system 16, such as, for example, rotational speedsensors, pressure sensors, flow rate sensors, acoustic sensors, etc. Thesensors may provide an input to the controller 104 related to theoperations of the various systems, including any reduced efficiencywithin the IPX 28. For example, the sensors may sense an increase in theamount of particulates within the lubrication fluid, which may preventthe lubrication fluid from properly lubricating the IPX 28. In responseto input from the sensors, the controller 104 may monitor and controlthe IPX 28 to determine any necessary operations changes to be made tothe filtration system 90. For example, the controller 104 may increasethe flow of lubrication fluid to the filtration system 90, increase thenumber of operational filters, increase or decrease the speed of thelubrication fluid flow within the filtration system 90, increase theamount of particulates removed from the lubrication fluid, and so forth.

In certain embodiments, the lubrication channel and the cleanlubrication fluid (e.g., lubrication fluid removed of particulates viathe filtration system) may be supplied through one or more apertures 110disposed along the axial axis 92. The one or more apertures 110 may runthrough the IPX body, such as through the IPX housing 102 and/or rotorsleeves 112. For example, the apertures 110 may be along the axial axis92 of the IPX 28 and/or positioned circumferentially about thecircumferential axis 96 of the IPX 28. For example, the IPX housing 102may have a first aperture 114 axially positioned between a first endcover 116 and the rotor 100 and a second aperture 118 axially positionedbetween a second end cover 120 and the rotor 100, such that the firstand second apertures 114 and 118 provides a channel through the IPXhousing 102. As a further example, the IPX housing 102 may include athird aperture 122 axially positioned along the rotor 100, such that itprovides a channel 124 through the IPX housing 102 and the rotor sleeve112. The one or more apertures 110 direct the clean lubrication fluidinto gaps between the rotor 100 and the rotor sleeve 112, and providelubrication fluid free of particulates for the lubrication of rotatingcomponents of the IPX 28. In certain embodiments, the end covers 116 and120 and one or more gaskets or 0-rings 126 may retain the cleanlubrication fluid within the gaps between the rotor 100 and the rotorsleeve 112.

In certain embodiments, the rotor 100 may be coupled to a motor 101 todrive the rotation of the rotor 100. The motor 101 may be coupled to thecontroller 104, such that the operation of the motor 101 is controlledby the controller 104 to regulate the operation and/or rotational speedof the rotor 100. The rotor 100 may be partially or entirely driven bythe motor 101. The motor 101 may be an electric motor, pneumatic drive,hydraulic drive, and so forth. In some embodiments, the pump (e.g., thehigh pressure pump 12 or a dedicated pump as will be discussed in FIGS.8-10) of the lubrication system 98 may be coupled to the motor 101. Assuch, the operation (e.g., pumping rate, speed, pressure, volume, etc.)of the pump may match the operation of the rotor 100. For example, theoperation of a positive displacement pump may be regulated to provide alubrication fluid flow rate that is proportional to the rotational speedof the rotor 100.

In certain embodiments, the lubrication fluid (e.g., the lubricationfluid prior to entering the filtration system 90 and/or the lubricationsystem 98, or the lubrication fluid after being treated by thefiltration system 90 and/or the lubrication system 98) may be routed(e.g., through internal or external routing paths to the IPX 28) to atemperature control system 99 to regulate (e.g., increase or decrease)the temperature of the lubrication fluid. The temperature control system99 may be any suitable heat exchanger. As will be discussed in moredetail, the lubrication fluid may serve to provide local and/or overallcooling or heating of the IPX 28.

FIG. 4 is a schematic diagram of an embodiment of the IPX 28 of FIG. 2,illustrating an embodiment of an integrated filtration system 130 with aplurality of filters 132. In the illustrated embodiment, the filtrationsystem 90 is integrated with the IPX housing 102. Furthermore, thefiltration system 90 receives a small portion 130 of the first fluid 18pumped by the high-pressure pump 12 from the total flow of thehigh-pressure fluid provided to the IPX 28. In this manner, the smallportion 134 of the first fluid 18 pumped to the IPX 28 is functioning asthe lubrication fluid may be filtered via a separate channel 136 beforebeing routed through the one or more apertures 110 to the gaps betweenthe rotor 100 and the rotor sleeve 112.

The filtration system 90 may utilize one or more different types offiltering techniques and may include one or more different types offiltering devices or equipment. For example, in certain embodiments, thefiltration system 90 includes one or more different types of filters,including cartridge filters, slow sand filters, rapid sand filters,pressure filters, bag filters, membrane filters, granular micro mediafilters, backwashable strainers, backwashable sand filters,hydrocyclones, and so forth. Furthermore, the filtration system 90 mayinclude a plurality of filters 132, including one or more filters ofeach type within the filtration system 90. In certain embodiments, thefilters 132 may be arranged around the axial axis 92, the radial axis94, the circumferential axis 96, or in any other combination. Forexample, the plurality of filters 132 may be arranged concentricallyaround the circumferential axis 96 of the filtration system 90. In otherembodiments, the plurality of filters 132 may be arranged in otherpatterns or arrangements, and may be spaced at a certain distance,randomly arranged, and so forth.

FIG. 5 is a schematic diagram of an embodiment of the integratedfiltration system 130 of FIG. 4, illustrating a settling filtrationsystem 140. For example, the settling filtration system 140 may includeone or more regions 142 where different types and sizes of particles 144accumulate, before being routed out of the settling filtration system140. In some embodiments, the settling filtration system 140 may includesettling tanks, cavities, reservoirs, containers, and so forth 141.Further, the cavity or tank 141 of the settling filtration system 140may be adjacent and/or surrounding the IPX 28. In the illustratedembodiment, the filtration system 90 may be integrated into the IPXhousing 102, as illustrated in FIG. 4. In particular, the filtrationsystem 90 may be the settling filtration system 140 that may extendalong a distance 146 of the body of the IPX 28. In some embodiments, thelength or distance 146 of the settling filtration system 140 may becustomized based on the type and/or degree of filtration desired for theIPX 28. In certain embodiments, the accumulated particles 142 (e.g.,particles filtered out of the lubrication flow) may be routed back intothe high-pressure fluid flow.

In the illustrated embodiment, the settling filtration system 140receives the small portion 134 of high-pressure fluid from the totalflow of the high-pressure fluid (e.g., the first fluid 18) provided tothe IPX 28, such as a small amount of high-pressure proppant free fluid(e.g., water). The small amount of high-pressure fluid may be utilizedas a lubrication fluid within the IPX 28. As noted above with respect toFIG. 4, the small portion 134 of the first fluid 18 pumped to the IPX 28that is functioning as the lubrication fluid may be filtered via theseparate channel 136 before being routed through the one or moreapertures 110 to the gaps between the rotor 100 and the rotor sleeve 112and/or to the gaps between other bearing or lubrication regions.Accordingly, it should be noted that in the illustrated embodiment, aportion of the total flow of the high-pressure fluid (e.g., the firstfluid 18) may not be filtered, while in other embodiments, additionalportions or the entire total flow of the high-pressure fluid may befiltered with the filtration system 90. In some embodiments, thisportion may be a small portion, while in others, this portion may be alarge portion of the entire total flow of the high-pressure fluid. Theportion of the total flow of the high-pressure fluid may be determinedby the amount of lubrication fluid desired.

The lubrication fluid may be processed through the settling filtrationsystem 140 to clean and remove any particles before the cleanlubrication fluid 91 is routed through the one or more apertures 110 tothe gap between the rotor 100 and the rotor sleeve 112. The settlingtank 141 may be a single tank or cavity, or may include one or moreseries of tanks, where each tank is configured to filter out varioussizes of particles 144. In certain embodiments, the lubrication fluidmay pass through the length of the settling tank 141 with a slow flowvelocity, such that the particles 144 settle out due to gravity. Forexample, in the illustrated embodiment, larger and coarser particles 148may settle out of the lubrication fluid first, followed by intermediateparticles 150 and/or finer particles 152. It should be noted thatintermediate particles 150 and/or finer particles 152 may settle out ofthe lubrication fluid based on the flow velocity and/or the length 146of the settling filtration system 140. For example, finer particles 152may be filtered through regions 142 of the settling filtration system140 where the flow velocity is very slow. In some embodiments, a portionof the lubrication fluid (e.g., excess lubrication fluid) as indicatedby arrows 154 may be routed to the flow of high-pressure fluid (e.g.,the first fluid 18) provide to the IPX 28

FIG. 6 is a schematic diagram of an embodiment of the filtration system90 of FIG. 3, illustrating a centrifugal separation filtration system160. In the illustrated embodiment, the filtration system 90 may beintegrated into the IPX housing 102, as illustrated in FIG. 4, and/orthe filtration system 90 may be external to the IPX components, asillustrated in FIG. 3. The centrifugal filtration system 160 may utilizecentripetal forces and fluid resistance to separate and/or sortparticles, thereby filtering and/or cleaning the lubrication fluidbefore providing the clean lubrication fluid 91 to the gap between therotor 100 and rotor sleeve 112 and/or to the gaps between other bearingor lubrication regions.

In certain embodiments, the centrifugal filtration system 160 mayinclude an inlet 162 configured to receive the small portion 134 ofhigh-pressure fluid (e.g., the first fluid 18) from the total flow ofthe high-pressure fluid provided to the IPX 28, such as a small amountof high-pressure proppant-free fluid (e.g., water). In otherembodiments, the inlet 162 may be configured to receive the smallportion 134 of high-pressure fluid directly from the high pressure pump12. The centrifugal filtration system 160 may include a variety ofgeometries, and may include a cyclone region 164 having a vortex and/orapex 166. In particular, the centrifugal filtration system 160 may beconfigured to remove particles suspended within the lubrication fluidthat are (more or) less dense than the surrounding fluid, and may do sobased on the characteristics of the fluid flow through the inlet and thegeometry of the cyclone region 164. In the illustrated embodiment,denser particles 168 may be removed at the apex 166 and routed back(e.g., indicated by an arrow 170) to the flow of high-pressure fluid(e.g., the first fluid 18) provide to the IPX 28. Further, the cleanedlubrication fluid may be at an overflow region 172 of the cyclone region164, and may be provided to the IPX 28 such that it is between the rotor100 and the rotor sleeve 112 and/or gaps between other bearing orlubrication regions. Indeed, the centrifugal filtration system 160 mayrequire no additional moving parts and/or maintenance, because anyunwanted particles filtered out of the lubrication fluid may be routedback to the first fluid 18 (e.g., high-pressure fluid).

FIG. 7 is a schematic diagram of an embodiment of the IPX 28 of FIG. 2,illustrating the filtration system 90 disposed within the rotor 100. Inthe illustrated embodiment, the filtration system 90 may be integratedinto the rotor 100 of the IPX 28. In particular, the filtration system90 may be incorporated into a central region 180 of the IPX 28, such asthrough cylindrical space within the rotor 100. In particular, thefiltration system 90 receives the small portion 134 of the first fluid18 pumped by the high-pressure pump 12 from the total flow of thehigh-pressure fluid provided to the IPX 28. Furthermore, the filtrationsystem 90 disposed through the rotor 100 may include one or morefiltration techniques/methods and/or one or more filtration devices,such as any of the ones described above with respect to FIGS. 3-6. Incertain embodiments, the filtration system 90 may utilize the rotationof the rotor 100 to enhance centrifugal separation. Once the lubricationfluid is filtered, the clean lubrication fluid 91 may exit the rotorregion of the IPX 28 via the one or more apertures 110, and may flow tothe gaps between the rotor 100 and the rotor sleeve 112 and/or to thegaps between other bearing or lubrication regions, as described above.

FIG. 8 is a block diagram of an embodiment of the IPX 28 of FIG. 2coupled to the lubrication system 98 to provide lubrication fluid to theIPX 28. In the illustrated embodiment, the lubrication system 98 mayinclude a dedicated fluid source 190 and a dedicated pump 192 (e.g.,external or internal pump) to pump a fluid from the fluid source 190 tothe IPX 28. The pump 192 may be a positive displacement pump or acentrifugal pump, and may be used in combination with one or morevalves. In particular, the pump 192 may increase the pressure of thefluid entering the IPX 28. The fluid provided by the fluid source 190may be a lubrication fluid and/or a flush fluid (e.g., flushing thebearing and seal areas of contaminants and/or particulates). In certainembodiments, the lubrication system 98 may include a filter and/orseparator 194 to filter and/or clean the fluid before the fluid entersthe IPX 28. The filter and/or separator 194 may be any suitablefiltration system set forth above (e.g., systems 90, 130, 140, and 160)or a combination thereof

FIG. 9 is a block diagram of an embodiment of the IPX 28 of FIG. 2coupled to the lubrication system 98 to provide lubrication fluid to theIPX 28. In the illustrated embodiment, the lubrication system 98includes the dedicated pump 192 as set forth above, and instead of thededicated fluid source 190, a fraction (e.g., the small portion 134) ofthe first fluid 18 is utilized as the lubrication fluid. In certainembodiments, the lubrication system 98 may include the filter and/orseparator 194 to filter and/or clean the portion of the small portion134 of the first fluid 18 before it enters the IPX 28. The filter and/orseparator 194 may be any suitable filtration system set forth above(e.g., systems 90, 130, 140, and 160) or a combination thereof. The pump192 may boost the pressure of the small portion 134 of the first fluid18. The pump 192 may provide pressure to overcome pressure losses frompassing through the filter and/or separator 194. The pump 192 mayprovide additional pressure to the fluid or lubrication fluid flowinginto the IPX 28.

It should be noted that the term “lubrication fluid” may serve severalfunctions or a combination thereof. First, the lubrication fluid mayserve to supply fluid bearings, such as to function as hydrostaticbearings, hydrodynamic bearings, or a combination thereof. Second, thelubrication fluid may serve to flush and/or clean seal areas, such asseals formed by narrow clearances in the IPX 28. Third, the lubricationfluid may serve to flush and/or clean debris or particles from thebearing areas. Fourth, the lubrication fluid may serve to provide localand/or overall cooling or heating of the IPX 28. Accordingly, severalpresent embodiments are directed to controlling fluids entering and/orflowing within the IPX 28 (e.g., controlling one or more fluid flowpaths) and/or operation of the IPX 28. For example, the lubricationfluid may flow to one or more of flow paths, such as flow paths of thefirst fluid 18, the second fluid 20, the high-pressure frac fluid 22,and the low-pressure frac fluid 23. For example, the lubrication fluidmay be controlled to enter the IPX 28 at a pressure equal to or greaterthan that of the first fluid 18.

With the foregoing in mind, FIG. 10 shows a block diagram of anembodiment of the lubrication system 98, operatively coupled to acontroller 200. In the illustrated embodiment, the lubrication fluidsystem 98 includes a fluid source 202, which may be the dedicated fluidsource 190 as discussed in the FIG. 8 or may be the small portion 134 ofthe first fluid 18 as discussed in FIG. 9. The lubrication fluid system118 also includes the pump 192 (e.g., a dedicated pump, internal orexternal) and may optionally include the filter and/or separator 194 asset forth above. It will be appreciated that at least a portion of theoperation of the IPX 28 and the operation of the lubrication fluidsystem 98 are controlled by the controller 200 to regulate the flowrate, flow volume, pressure, and/or temperature of the lubrication fluidand/or other fluids (e.g., the first fluid 18) depending on routing ofthe lubrication fluid (e.g., flow path and where the lubrication fluidenters the IPX 28).

The controller 200 includes a memory 204 (e.g., a non-transitorycomputer-readable medium/memory circuitry) storing one or more sets ofinstructions (e.g., processor-executable instructions) implemented tocontrol or regulate at least a portion of the operation of the IPX 28and the operation of the lubrication system 98. The controller 200 alsoincludes one or more processor 206 configured to access and execute theone or more sets of instructions encoded by the memory 204, associatedwith at least a portion of the operation of the IPX 28 and the operationof the lubrication system 98. The memory 204 may include volatilememory, such as random access memory (RAM), and/or non-volatile memory,such as read-only memory (ROM), optical drives, hard disc drives, orsolid-state drives. The one or more processor 206 may include one ormore application specific integrated circuits (ASICs), one or more fieldprogrammable gate arrays (FPGAs), one or more general purposeprocessors, or any combination thereof. Furthermore, the term processoris not limited to just those integrated circuits referred to in the artas processors, but broadly refers to computers, processors,microcontrollers, microcomputers, programmable logic controllers,application specific integrated circuits, and other programmablecircuits.

Furthermore, the controller 200 may be communicatively coupled to one ormore sensors 208 to collect data related to fluid flow, such as flowrate, flow volume, pressure, temperature of the lubrication fluid, thefirst fluid 18, the second fluid 20, the main process fluid (e.g.,cleaned or filtered first fluid 18 and/or second fluid 20), etc. The oneor more sensors 208 may include but not limited to pressure sensors,temperature sensors, flow meters, and flow sensors. The one or moresensors 208 may be disposed at any suitable locations along the fluidflow paths to obtain data related to the fluid flow of interest uponreceiving instruction(s) or control signal(s) from the controller 200.In some embodiments, the controller 200 and the controller 104 (in FIG.3) are the same controller.

The pressure of the lubrication fluid entering the IPX 28 may depend onthe pressure of the first fluid 18 as in FIG. 9 (e.g., the small portion134 of the first fluid 18 is routed to serve as the lubrication fluid)and/or may depend on the pressure of the fluid flowing out of the pump192 as in FIGS. 8 and 9. In addition, the pressure of the lubricationfluid entering the IPX 28 may depend on the operation of the filterand/or separator 194. For example, the fluid passing through the filterand/or separator 194 may experience certain pressure losses. As such, tocontrol or regulate the pressure of the lubrication fluid entering theIPX 28, in one embodiment, to control the pressure of the first fluid 18and/or pressure the small portion 134 of the first fluid 18 routed toserve as the lubrication fluid, the controller 200 is operativelycoupled to one or more valves disposed along the flow path of the firstfluid 18, along the flow path of the small portion 134 of the firstfluid 18, the high pressure pump 12, or a combination thereof. In oneembodiment, the controller 200 is operatively coupled to the pump 192 tocontrol or regulate the pressure of the fluid flow (e.g., lubricationfluid) out of the pump 192. In one embodiment, the controller 200 maycontrol or regulate the pump 192 to increase pressure to overcomepressure losses at the filter and/or separator 194.

In certain embodiments, the pump 192 as shown in FIGS. 8-10 may becoupled to the motor 101. As such, the operation (e.g., pumping rate,speed, pressure, volume, etc.) of the pump 192 may be regulated to matchthe operation of the rotor 100. For example, the pump 192 may be adisplacement pump and may be regulated to provide a lubrication fluidrate that is proportional to the rotational speed of the rotor 100.

Further, the controller 200 may control or regulate the lubricationfluid flow (e.g., flow rate, flow volume) into the IPX 28 depending onthe routing of the lubrication fluid (e.g., where the lubrication fluidenters the IPX 28) as will be discussed in FIG. 11. FIG. 11 showspartial circuit diagrams of the lubrication fluid. In the illustratedembodiment, a resistance symbol 210 represents the resistance (e.g.,flow resistance) of the lubrication fluid path or other fluidresistance, an arrow represents the flow direction, and a circle symbolrepresents a pressure of a location interest. In particular, a circle212 represents the pressure of the lubrication fluid at an inlet intothe IPX 28, a circle 214 represents the pressure of the first fluid 18at the high pressure fluid inlet into the IPX 28, a circle 216represents the pressure of the fluid within the IPX 28 wherein there maybe mixing between the first fluid 18 and the second fluid 20, and acircle 218 represents the pressure of the second fluid 20 at the the lowpressure fluid inlet into the IPX 28.

In an example partial circuit diagram 220, the lubrication fluid flowsto an internal region of the IPX 28 where the pressure 216 is anintermediate value between the pressure 214 and the pressure 218.Accordingly, the pressure of lubrication fluid 212 may be higher orlower than the pressure 214. In another example partial circuit diagram222, the lubrication fluid may flow to any of the internal region of theIPX 28, the high pressure inlet of the first fluid 18, the low pressureinlet of the second fluid 20, or a combination thereof. Accordingly, itmay be desirable for the lubrication fluid to have a pressure (e.g., thepressure 212) that is equal to or greater than the pressure 214. Itshould also be noted that as the flow rate of the fluid increases, thepressure downstream (e.g., the point where fluids merge) would tend toincrease as a higher volume of fluid is flowing through per given time.In certain embodiments, the resistance(s) may be negligible between thepressure 212 at the lubrication fluid inlet and the pressure 214 at thehigh pressure inlet of the first fluid 18, and in this case, an increasein the pressure or flow rate of the lubrication fluid may essentiallydisplace the first fluid 18.

Accordingly, the controller 200 may control or regulate the operation ofthe corresponding components of the IPX 28 and components of thelubrication fluid system 98 (e.g., one or more valves, the high pressurepump 12, the low pressure pump 14, the pump 192, etc.) to increase ordecrease the pressure, flow rate, flow volume, or a combination thereof,at least in part based on the concepts discussed in the partial circuitdiagrams 220 and 222. For example, in the case that the lubricationfluid is routed to enter the internal region of the IPX 28, thecontroller 200 may control the pump 192 and/or corresponding valve(s) toregulate the pressure of the lubrication fluid 212 to be higher or lowerthan the pressure 214. For example, in the case that the lubricationfluid is routed to enter any of the internal region of the IPX 28, thehigh pressure inlet of the first fluid 18, and/or the low pressure inletof the second fluid 20, or a combination thereof, the controller 200 maycontrol the pump 192 and/or corresponding valve(s) to increase thepressure of the lubrication fluid such that the pressure of thelubrication fluid is equal to or greater than the pressure of the firstfluid 18 at the high pressure inlet.

In some embodiments, a control algorithm may be stored in the memory 204and executable by the processor 206 of the controller 200. The controlalgorithm upon execution may modulate the flow rates of respectivefluids (e.g., fluid pumped out by the pump 92, the small portion 134 ofthe first fluid 18) proportional to the operating pressure of the IPX 28or some function of the operating pressure of the IPX 28 in order tosupply a suitable amount of the lubrication fluid to the IPX 28. In someembodiments, the controller 200 may change the flow rate or pressure ofthe lubrication fluid in response to other variables, such as theperformance or operating condition of the IPX 28. For example, if theperformance of the IPX 28 decreases as a result of contaminatedbearings, the controller 200 may control the flow rates of respectivefluids (e.g., fluid pumped out by the pump 192, the small portion 134 ofthe first fluid 18) to increase the flow volume and/or flow rate oflubrication fluid into the IPX 28. In some embodiments, the controller200 may control the flow rates of respective fluids (e.g., fluid pumpedout by the pump 92, the small portion 134 of the first fluid 18) basedon operating condition of the IPX, such as temperatures (e.g., measuredtemperature or expected temperature), to provide adequate cooling orheating to the IPX 28. In some embodiments, the controller 200 maycontrol the temperature of respective fluids (e.g., fluid pumped out bythe pump 92, the small portion 134 of the first fluid 18) based ontemperatures (e.g., expected temperatures or temperatures measured viathe one or more sensors 208) in the IPX 28 to provide adequate coolingor heating to the IPX 28.

As set forth above, the controller 200 may increase the fluid flow ratevia controlling the pump 192 (e.g., a positive displacement pump,centrifugal pump) and/or via controlling one or more valves disposedalong the respective flow path(s). In some embodiments, the controller200 may also control the pump 192 and/or respective valves to cause anexcess flow which overflows into the main process fluid (e.g., cleanedor filtered first fluid 18 and/or second fluid 20). FIG. 12 is aschematic diagram of an embodiment of the IPX 28 coupled to thelubrication system 98. In the illustrated embodiment, the lubricationfluid provided by the lubrication system 98 flows into the IPX 28 asindicated by arrows 230. As illustrated in diagram 232, the IPX 28includes at one or more gaskets, O-rings, or other suitable seals 126disposed between the first end cover 116 and the IPX housing 102 andbetween the second end over 120 and the IPX housing 102 on both axialends, such that the lubrication fluid is separated or isolated from themain process fluid (e.g., cleaned or filtered first fluid 18 and/orsecond fluid 20). As illustrated in diagram 234, one of the one or moregaskets, 0-rings, or other suitable seals 126 disposed between the firstend cover 116 and the IPX housing 102 is replaced by a valve 236, suchthat the lubrication fluid may contact or communicate with the mainprocess fluid (e.g., cleaned or filtered first fluid 18 and/or secondfluid 20) depending on the operation of the valve 236 (e.g., open/closeposition of the valve). In some embodiments, the valve 236 is a checkvalve to allow overflow of lubrication fluid into the main process fluidbut not flow in the reverse direction. In some embodiments, the valve236 is a pressure relief valve to adjust or limit the pressure of thelubrication fluid. As may be appreciated, if the lubrication fluid isprovided to the IPX 28 via separate flow paths such that the lubricationfluid is separated or isolated from the main process fluid (e.g., asillustrated in diagram 232), the pressure of the lubrication fluid maybe mainly controlled via operation of the pump 192. However, if thelubrication fluid is in contact or communication with the main processfluid (e.g., as illustrated in diagram 234), the pressure of thelubrication fluid may be affected by the operation of the pump 192, theoperation of the valve 236, the pressure of the main process fluid, or acombination thereof.

While the invention may be susceptible to various modifications andalternative forms, specific embodiments have been shown by way ofexample in the drawings and have been described in detail herein.However, it should be understood that the invention is not intended tobe limited to the particular forms disclosed. Rather, the invention isto cover all modifications, equivalents, and alternatives falling withinthe spirit and scope of the invention as defined by the followingappended claims.

1. A system, comprising: a hydraulic energy transfer system configuredto exchange pressures between a first fluid and a second fluid, whereinpressure of the first fluid is greater than pressure of the secondfluid; and a lubrication system coupled to the hydraulic energy transfersystem and configured to pump or direct a lubrication fluid into thehydraulic energy transfer system.
 2. The system of claim 1, comprising afiltration system coupled to the hydraulic energy transfer system andconfigured to filter the lubrication fluid before the lubrication fluidenters the hydraulic energy transfer system
 3. The system of claim 1,wherein the hydraulic energy transfer system is a rotary isobaricpressure exchanger (IPX) system.
 4. The system of claim 1, wherein thefirst fluid hydraulically acts upon the second fluid to increase thepressure of the second fluid that is driven out of the hydraulic energytransfer system for utilization in a downstream application.
 5. Thesystem of claim 1, wherein the lubrication fluid comprises a lubricationfluid supplied by a fluid source external to the hydraulic energytransfer system.
 6. The system of claim 1, wherein the lubrication fluidcomprises a fraction of the first fluid.
 7. The system of claim 6,wherein the filtration system is integrated with a housing of thehydraulic energy transfer system.
 8. The system of claim 6, wherein thefiltration system comprises a settling filtration system, a centrifugalseparation filtration system, or a filtration system disposed within arotor of the hydraulic energy transfer system.
 9. The system of claim 1,comprising a controller programmed to control one or more valves and/orthe one or more pumps of the system to selectively route the lubricationfluid based on an operating condition of the system.
 10. The system ofclaim 9, wherein a control algorithm is stored in a memory of thecontroller and upon execution may modulate flow rates of the firstfluid, the second fluid, the lubrication fluid, or a combinationthereof, based at least in part on an operating pressure or performanceof the hydraulic energy transfer system.
 11. The system of claim 1,wherein the lubrication system comprises a dedicated pump to route thelubrication fluid into the hydraulic energy transfer system.
 12. Asystem, comprising: a hydraulic energy transfer system configured toexchange pressures between a first fluid and a second fluid, whereinpressure of the first fluid is greater than pressure of the secondfluid; a lubrication system coupled to the hydraulic energy transfersystem and configured to pump or direct a lubrication fluid into thehydraulic energy transfer system; a filtration system coupled to thehydraulic energy transfer system and configured to filter thelubrication fluid before the lubrication fluid enters the hydraulicenergy transfer system; one or more valves and one or more pumpsdisposed along fluid flow paths of the system; and a controllerprogrammed to control the one or more valves and/or the one or morepumps of the system to selectively route the lubrication fluid into thehydraulic energy transfer system based on operating condition of thesystem.
 13. The system of claim 12, comprising one or more sensorsdisposed along the one or more fluid paths of the system to collectfluid data related to operating condition of the system.
 14. The systemof claim 12, wherein the fluid data comprises flow rate, flow volume,pressure, temperature, or a combination thereof.
 15. The system of claim12, wherein the lubrication fluid comprises a lubrication fluid that isa fraction of the first fluid, and the lubrication system comprises adedicated pump to route the lubrication fluid into the hydraulic energytransfer system.
 16. The system of claim 12, comprising a temperaturecontrol system configured to regulate temperature of the lubricationfluid.
 17. A system, comprising: a hydraulic energy transfer systemconfigured to exchange pressures between a first fluid and a secondfluid, wherein pressure of the first fluid is greater than pressure ofthe second fluid; a lubrication system coupled to the hydraulic energytransfer system and comprises a dedicated pump to direct a lubricationfluid into the hydraulic energy transfer system; a filtration systemcoupled to the hydraulic energy transfer system and configured to filterthe lubrication fluid before the lubrication fluid enters the hydraulicenergy transfer system, wherein the lubrication fluid comprises afraction of the first fluid or a fluid from a fluid supply sourceexternal to the hydraulic energy transfer system; and a controllerprogrammed to control one or more valves and/or one or more pumpsdisposed along fluid flow paths of the system to selectively route thelubrication fluid into the hydraulic energy transfer system based on anoperating condition of the system.
 18. The system of claim 17, whereinthe controller is programmed to control the one or more valves, the oneor more pumps, or a combination thereof, to route the lubrication fluidto cool one or more heated regions, to heat one or more cold regions ofthe hydraulic energy transfer system, to lubricate bearings of thehydraulic energy transfer system, or to flush debris or particles fromcomponents of the hydraulic energy transfer system.
 19. The system ofclaim 17, wherein the controller is programmed to regulate pressure ofthe lubrication fluid to be higher or lower than pressure of the firstfluid when the lubrication fluid is routed to enter an internal regionof the hydraulic energy transfer system.
 20. The system of claim 17,wherein the controller is programmed to regulate pressure of thelubrication fluid to be equal to or greater than pressure of the firstfluid when the lubrication fluid is routed to merge with the firstfluid.